US20090289422A1 - Packing ring combination - Google Patents

Packing ring combination Download PDF

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Publication number
US20090289422A1
US20090289422A1 US12/292,220 US29222008A US2009289422A1 US 20090289422 A1 US20090289422 A1 US 20090289422A1 US 29222008 A US29222008 A US 29222008A US 2009289422 A1 US2009289422 A1 US 2009289422A1
Authority
US
United States
Prior art keywords
ring
sealing
packing
pressure
segments
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US12/292,220
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English (en)
Inventor
Tino Lindner-Silwester
Christian Hold
Alexander Jandl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hoerbiger Kompressortechnik Holding GmbH
Original Assignee
Hoerbiger Kompressortechnik Holding GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hoerbiger Kompressortechnik Holding GmbH filed Critical Hoerbiger Kompressortechnik Holding GmbH
Assigned to HOERBIGER KOMPRESSORTECHNIK HOLDING GMBH reassignment HOERBIGER KOMPRESSORTECHNIK HOLDING GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HOLD, CHRISTIAN, JANDL, ALEXANDER, LINDNER-SILWESTER, TINO
Publication of US20090289422A1 publication Critical patent/US20090289422A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
    • F16J15/24—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings with radially or tangentially compressed packing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/26—Sealings between relatively-moving surfaces with stuffing-boxes for rigid sealing rings

Definitions

  • the present invention relates to a packing ring combination with a sealing ring consisting of a number of sealing and back-up segments, the sealing and back-up segments being arranged next to one another alternately in the circumferential direction to form a ring, and with a stop ring which rests axially against the sealing ring, and to a pressure packing and to a seal with such a packing ring combination.
  • Piston compressors in particular of double-acting construction, require sealing of the crank-side compression chamber in the cylinder, in which the (high) cylinder pressure p cyl variable over time prevails, along the oscillating piston rod 5 .
  • This sealing has typically to proceed against the (low) ambient pressure p a prevailing in the crankcase.
  • the sealing elements which are used for such a seal 4 are known as packing rings 6 , 7 and are arranged in a “pressure packing” 2 , consisting as a rule of a number of packing rings 6 , 7 , as illustrated by way of example in a conventional embodiment in FIG. 1 .
  • the sealing elements may then follow unavoidable lateral movements of the piston rod 5 without losing their sealing effect.
  • a plurality of such packing rings 6 , 7 are connected in series in a pressure packing 2 , with a plurality of pressure packings 2 as a rule being arranged in succession to form a seal 4 .
  • Such pressure packings 2 or seals 4 are sufficiently well known from the prior art in a very wide range of configurations, e.g. from GB 928 749 A or U.S. Pat. No. 1,008,655 A.
  • Packing rings 6 , 7 are self-activating seals, which need as a rule a certain pressure differential p 1 -p 2 requiring sealing for a sufficient sealing effect to be achieved, i.e. sufficiently low leakage ( FIG. 1 c ).
  • the gas pressure in a packing chamber 3 breaks down in the gaps to be sealed of a packing ring 6 , 7 from the higher level p 1 to the lower level p 2 in the next packing chamber 3 .
  • FIG. 1 c is a schematic diagram of this pressure breakdown in the sealing gap formed between packing ring 6 , 7 and piston rod 5 .
  • This sealing gap has a significant part to play with regard to the performance of the packing rings 6 , 7 , since the relative motion of the contact surfaces between piston rod 5 and rings 6 , 7 causes wear to the packing rings 6 , 7 .
  • This ring wear generally requires cut ring types, which enable automatic, continuous readjustment of the ring in the event of material abrasion at this ring/piston rod sealing gap.
  • Standard in the industry are radially and tangentially cut rings 6 , 7 , which are used in pairs in packing chambers of the pressure packing in order to cover one another at the butt gaps arising for the purpose of wear compensation, as shown schematically in FIG. 1 b .
  • Such combinations of radially/tangentially cut rings are single-acting seals, which seal only in the direction of the crosshead, while in the course of the crank-side reexpansion phase of the piston compressor 1 the radial cuts ensure that no relatively high pressure can be trapped in the packing.
  • garter springs circumferential springs 9 wound over the outer circumference, which springs press the packing rings 6 , 7 against the piston rod 5 even in the unpressurized state.
  • sealing relative to the piston rod is effected substantially only by the tangentially cut packing ring, whose ring segments may be pushed together under wear due to the tangential cut arrangement and thus maintain the sealing effect.
  • the radially cut packing ring serves substantially only to seal the wear gaps of the tangential packing ring in the axial and radial directions and is subject to low wear only in the running-in phase.
  • the radial packing ring is then worn only until the ring segments lie against one another in the circumferential direction. The radially and tangentially cut packing rings thus wear differently.
  • the tangentially cut ring In addition to the circumstance that the tangentially cut ring always wears faster due to greater surface pressure than the radially cut ring, the tangential ring is typically also subject to uneven wear in the circumferential direction, which may be accompanied by opening of the tangential cuts and thus significantly increased leakage. Thus, such a ring may lose the majority of its sealing effect even if it has not yet reached its wear limit (brought about by the wear compensation gap). Furthermore, under increasing wear a packing ring combination of radially and tangentially cut packing rings requires resilient deformation of the ring segments, in order to be able to maintain the sealing effect. Thus, the only materials feasible for such packing ring combinations are those which allow appropriate resilient deformation.
  • JP 05-044850 A1 has already proposed the use of a six-part sealing ring, which comprises three sealing segments, which form a continuous sealing surface radially on the inside.
  • the sealing segments rest against wedge-shaped back-up segments arranged therebetween.
  • the sealing segments move radially inwards and in so doing slide over the back-up segments, which remain in substantially the same position.
  • Such a sealing ring may therefore be subject to very considerable wear without losing its sealing effect.
  • the problem with this is that the sealing ring has to be changed in good time, before the sealing segments wear away too much and are thereby possibly damaged or even destroyed by the mechanical and/or thermal loading. Since the actual wear cannot be detected from outside, however, the seal has to be checked regularly, which is generally also accompanied by (premature) replacement of the sealing rings. The service life of the sealing rings may therefore possibly not be optimally utilized.
  • an axial shoulder is provided on the sealing segments of the sealing ring, which shoulder at least partially overlaps the stop ring in the axial direction, and the axial shoulder is arranged at a distance from the stop ring in the radial direction, such that the axial shoulder rests against the stop ring once the sealing segments have been worn by a given amount.
  • the sealing effect is based, in the case of the embodiment according to the invention, on the fact that no resilient deformation is necessary with increasing wear as in the case of conventional radially/tangentially cut rings and thus the opening up of leakage gaps or paths may be prevented. Because maintenance of the sealing effect is not based on any resilient deformation, this design is also very particularly suitable for high performance plastics such as polyimide for example, which combines the best frictional and wear characteristics with high mechanical strength and rigidity as well as heat resistance.
  • the embodiment according to the invention of the sealing ring is additionally exceptionally insensitive to dimensional variations during manufacture.
  • a radially cut packing ring which rests axially against the sealing ring on the axial end face of the sealing ring facing the high pressure.
  • the distinctive feature of this design consists in the fact that the sealing ring, which is pressed, due to the relatively low gas pressure in the sealing gap, with greater force than the radially cut packing ring against the component to be sealed and is thus also subject to greater wear, may suffer considerable material abrasion at its internal diameter without losing its sealing effect. Due to this forced symmetrical wear to the sealing segments, the sealing ring material is optimally utilized and a maximum service life is achieved with a given rate of wear, while on the other hand the service life of the sealing ring may be extended by a simple increase in the radial height of the sealing segments.
  • the axial shoulder is provided on the side of the sealing ring facing the low pressure.
  • the stop ring may then be either rigid or resilient.
  • the stop ring may, for this purpose, take the form of a rigid back-up ring, which rests axially against the sealing ring on the low pressure side and which is surrounded at least in part by the axial shoulder, or of a resilient ring, which rests axially against the sealing ring on the low pressure side and which is surrounded at least in part by the axial shoulder.
  • a resilient ring may also be arranged between axial shoulder and back-up ring.
  • the axial shoulder may also be provided on the side of the sealing ring facing the high pressure.
  • the stop ring may then advantageously be the radially cut packing ring itself or a rigid back-up ring on the high pressure side, which rests axially against the sealing ring.
  • Use of the radially cut packing ring as a stop means is very particularly advantageous, since then the sealing ring and the radially cut packing ring arranged upstream thereof wear at the same rate after a given radial wear of the sealing ring, which may be set as desired.
  • the problem of the sealing ring always wearing more rapidly than the radially cut packing ring arranged upstream thereof is thus eliminated and the available ring material is utilized optimally for wear. Wear retardation may consequently also be achieved thereby.
  • FIG. 1 shows known sealing of a piston rod with radially and tangentially cut packing rings
  • FIGS. 2 and 3 show an advantageous arrangement of a packing ring combination or a pressure packing
  • FIGS. 4 and 5 show advantageous developments of a sealing ring of a packing ring combination according to the invention with bevelled edges and
  • FIGS. 6 to 9 show further advantageous developments of a packing ring combination or a pressure packing.
  • a packing ring combination according to the invention of a pressure packing 26 , e.g. a seal for a piston rod 5 of a compressor.
  • the pressure packing 26 is here arranged in a packing chamber 3 of a packing housing (e.g. formed by adjoining chamber discs 10 ) and here provides a seal between a side with a high pressure p 1 and a side with a low pressure p 2 . Sealing in this context means that the high pressure p 1 is broken down by the pressure packing 26 or the packing ring combination to the low pressure p 2 .
  • the packing ring combination consists of a sealing ring 12 , which in this example is of eight-part construction, and a stop ring 20 .
  • the sealing ring 12 comprises an axial shoulder 16 , here in the radially outer area of the sealing ring 12 and facing the side with the high pressure p 1 .
  • This axial shoulder 16 may here be arranged solely on the sealing segments 14 or on both the sealing segments 14 and the back-up segments 13 .
  • the sealing ring 12 lies with the opposing, low-pressure-side axial end face against the wall of the packing housing 10 and so provides a seal in the radial direction against the high pressure p 1 acting in the packing chamber 3 .
  • the stop ring 20 takes the form in this example of a radially cut packing ring 30 and lies axially against the sealing ring 12 on the high pressure side.
  • the axial shoulder 16 of the sealing ring 12 thus at least partially overlaps the stop ring 20 in the axial direction.
  • the inner circumferential surface 17 of the axial shoulder 16 and the outer circumferential surface 19 of the stop ring 20 are here arranged at a distance from one another in the radial direction, the stop ring 20 being arranged radially on the inside relative to the circumferential surface 17 of the axial shoulder 16 .
  • the stop ring 20 could however also be embodied by a rigid back-up ring instead of a radially cut packing ring 30 , which rigid back-up ring rests axially against the sealing ring 12 on the high pressure side.
  • the axial shoulder 16 of the sealing ring 12 would then come to lie against the outer circumferential surface of the back-up ring after a certain amount of wear.
  • a six-part sealing ring 12 is illustrated in FIG. 4 and comprises in this exemplary embodiment in each case three sealing segments 14 and three back-up segments 13 , which are arranged lying alternately against one another in the circumferential direction and form a ring. Radially to the inside there arises a continuous circular circumferential surface 11 , which at the same time forms the sealing surface relative to the component to be sealed, here for example the piston rod 5 .
  • the high pressure p 1 is broken down to the low pressure p 2 along this sealing surface.
  • At the radially outer circumferential surface of the sealing ring 12 or the sealing segments 14 and the back-up elements 13 it is possible, in a known manner, to provide a recess for accommodating a circumferential spring 9 .
  • the two end faces 21 , viewed in the circumferential direction, of the sealing segments 14 are preferably parallel to one another.
  • the back-up elements 13 Upon wear of the sealing segments 14 , whereby the sealing segments 14 are advanced radially inwards by the radially externally acting high pressure p 1 , the back-up elements 13 thereby remain substantially in position and the sealing segments 14 slide radially inwards over the back-up segments 13 .
  • the two end faces of a sealing segment 14 may also be at an angle to one another.
  • the back-up segments 13 may however also be moved in the radial direction by wear of the sealing segments 14 . It must therefore be ensured in such an embodiment, for example by constructional design of the back-up segments 13 , that the inner circumferential surface 11 remains closed, in order to be able to maintain the sealing effect of the sealing ring 12 .
  • the end faces 21 viewed in the circumferential direction, of the sealing segments 14 to be bevelled radially on the inside, e.g. by a radial cut 24 , as illustrated in FIG. 5 by means of an eight-part sealing ring 12 .
  • the back-up segments 13 may likewise be bevelled radially on the inside, e.g. by a tangential cut 25 .
  • the sealing segments 14 Upon installation of the sealing ring 12 , the sealing segments 14 are compressed by the circumferential spring 9 to a predetermined internal diameter, which is defined by the bevel of the sealing segments 14 , and rest against one another at the bevels, whereby a defined installation situation is achieved.
  • a radially cut packing ring 30 may be arranged for this purpose on the high pressure p 1 side to seal this gap 22 , which packing ring rests axially against the sealing ring 12 . Such an advantageous arrangement is illustrated in FIGS. 2 and 3 and described below.
  • the radially cut packing ring 30 in this case at the same time the stop ring 20 , is here arranged in the axial recess formed by the axial shoulder 16 and rests axially against the sealing ring 12 .
  • the radially cut packing ring 30 is thus at least partially enclosed in the circumferential direction by the axial shoulder 16 .
  • the radially cut packing ring 30 which is to this end advantageously of at least three-part construction, is then also carried along by the sealing ring 12 and pressed together with the sealing ring 12 against the component to be sealed and thus wears jointly with the sealing ring 12 . Because of the then markedly enlarged contact surface, the rate of wear thereby slows down considerably, so achieving wear retardation. Thus, reliable functioning of the seal, at least for a certain period, may still be ensured even when the limit stop has already been reached.
  • the radially cut packing ring 30 in FIG. 3 a packing ring 30 with four packing ring segments 32 , then needs to be arranged in such a way that the radial gaps 33 arising between the packing ring segments 32 are offset relative to the axial gaps 22 in the sealing ring 12 , in order to seal the latter, as illustrated in FIG. 3 .
  • an antirotation element is advantageously also provided, in order to maintain the offset.
  • the antirotation element may be a simple pin, which is pressed into aligned openings in the sealing ring 12 and in the stop ring 20 . However, any other suitable antirotation element is also feasible.
  • any antirotation element between sealing ring 12 and stop ring 20 is arranged particularly advantageously on one of the back-up segments 13 , since the antirotation element is in this case subject to substantially no shear stress upon wear of the sealing segments 14 and thus the risk of breakage of the antirotation element is slight.
  • FIGS. 6 and 7 A further advantageous development of the invention is illustrated in FIGS. 6 and 7 .
  • the axial shoulder 16 of the sealing ring 12 is disposed on the low pressure p 2 side.
  • a rigid, uncut back-up ring 40 rests axially against the low pressure p 2 side of the sealing ring 12 as the stop ring 20 .
  • the back-up ring 40 is here arranged between the sealing ring 12 and a wall of the packing housing 10 and takes on the task of radially sealing the sealing ring 12 against the high pressure p 1 prevailing in the packing chamber 3 .
  • the back-up ring 40 is in this case preferably wider than the length of the axial shoulder 16 , as indicated in FIG.
  • a resilient ring 41 is additionally arranged against the low pressure end face of the sealing ring 12 , this being arranged radially between back-up ring 40 and axial shoulder 16 .
  • This resilient ring 41 is preferably spaced radially from the inner circumferential surface 17 of the axial shoulder 16 and may also be radially spaced from the outer circumferential surface 42 of the back-up ring 40 .
  • the resilient ring 41 also comes at some point to rest on the back-up ring 40 , which further slows down the rate of wear. The rate of wear may thus be gradually reduced, until no further wear is possible.
  • the wear retardation, brought about by the radial give of the resilient ring 41 may be adjusted by the radial height of and/or the material used for the resilient ring 41 . It is also feasible, however, for the resilient ring 41 to rest from the outset against the axial shoulder 16 , whereby the wear retardation arises from the outset.
  • Such a resilient ring 41 may of course also be used without any additional back-up ring 40 and in this case simultaneously forms the stop ring 20 .
  • the sealing ring 12 preferably lies for the purpose of radial sealing against the wall of the packing housing 10 and the resilient ring 41 is spaced radially from the axial shoulder 16 .
  • a radially cut packing ring 30 is not, however, limited only to developments with axial gaps 22 between the sealing segments 14 of the sealing ring 12 . It is also possible for such a radially cut packing ring 30 to be used in the various arrangements in an embodiment of the sealing ring 12 according to FIG. 4 , in particular and particularly advantageously in conjunction with an axial shoulder 16 facing the high pressure side, as described in FIGS. 2 and 3 . In this case, a rigid back-up ring on the high pressure side could also be provided as the stop ring 20 instead of the radially cut packing ring 30 .
  • the axial shoulder 16 of the sealing ring 12 does not of course have to be arranged in the radially outer area of the sealing ring 12 , but rather may also for example be arranged in the middle or in the radially inner area, provided that it is initially arranged radially spaced from the stop ring 20 .
  • the radial spacing serves, primarily in association with wear retardation, substantially to allow a running-in phase, during which the sealing segments 14 may wear without hindrance and in this way become conformed to the component to be sealed.
  • the radial spacing may preferably be between 0.5 mm and 2 mm.
  • the sealing ring 12 according to the invention is preferably used in a pressure packing 26 .
  • a plurality of such pressure packings 26 may also be arranged axially one behind the other to produce a seal 4 , for example as in FIG. 1 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
US12/292,220 2007-11-15 2008-11-13 Packing ring combination Abandoned US20090289422A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA1853/2007 2007-11-15
AT0185307A AT505293B1 (de) 2007-11-15 2007-11-15 Packungsring-kombination

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US20090289422A1 true US20090289422A1 (en) 2009-11-26

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US12/292,220 Abandoned US20090289422A1 (en) 2007-11-15 2008-11-13 Packing ring combination

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US (1) US20090289422A1 (zh)
EP (1) EP2060833A1 (zh)
CN (1) CN101435507A (zh)
AT (1) AT505293B1 (zh)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150014945A1 (en) * 2013-07-12 2015-01-15 GM Global Technology Operations LLC Back-Up Ring Design "Split & Close"
US8985588B2 (en) 2010-08-31 2015-03-24 Burckhardt Compression Ag Seal arrangement
CN105899859A (zh) * 2013-12-23 2016-08-24 伯克哈特压缩机股份公司 密封环
CN107701728A (zh) * 2017-11-07 2018-02-16 上海东方压缩机制造有限公司 压力平衡式填料环
KR20200123018A (ko) * 2019-04-18 2020-10-28 에어 프로덕츠 앤드 케미칼스, 인코오포레이티드 환형 실링 조립체

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2891982T3 (es) * 2013-12-10 2022-02-01 Howden Thomassen Compressors B V Caja de empaquetadura con anillo de sellado único
CN105587862B (zh) * 2016-02-05 2019-05-24 沈阳耐蚀合金泵股份有限公司 应用于旋转机械的轴面机械密封
CN105805316B (zh) * 2016-06-06 2018-05-08 珠海格力节能环保制冷技术研究中心有限公司 轴密封结构及压缩机
CN113417586A (zh) * 2021-04-24 2021-09-21 才艳梅 井口高压循环导龙头

Citations (6)

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Publication number Priority date Publication date Assignee Title
US670565A (en) * 1899-07-29 1901-03-26 Edwin Reynolds Piston-rod packing.
US1165486A (en) * 1911-11-15 1915-12-28 Robert Allen Packing for rods and the like.
US1819559A (en) * 1929-08-17 1931-08-18 British Metallic Packings Comp Metallic packing for reciprocating shafts
US3711104A (en) * 1971-03-16 1973-01-16 Dresser Ind Seal assembly
US3972640A (en) * 1974-09-16 1976-08-03 Miller Raphael W Highway joint with spring torsion bar
US6439578B1 (en) * 2000-04-10 2002-08-27 Hoerbiger Ventilwerke Gmbh Sealing ring combination

Family Cites Families (9)

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US1008655A (en) 1910-11-19 1911-11-14 John H Lewis Metallic packing for piston-rods.
GB273993A (en) * 1927-02-23 1927-07-14 British Metallic Packings Comp Improved metallic packing for stuffing-boxes
DE503087C (de) * 1927-10-26 1930-07-22 Gustav Huhn Packungsring
GB320291A (en) * 1928-12-31 1929-10-10 Gustav Huhn Improvements in and relating to metallic packing-rings for piston rods and shafts
GB928749A (en) 1960-07-28 1963-06-12 Union Carbide Corp Improvements in or relating to seals
US3305241A (en) 1965-10-19 1967-02-21 Cooper Bessemer Corp Packing ring structure
US3817517A (en) * 1973-03-15 1974-06-18 Foerenade Fabriksverken Device for establishing a seal between cylindrical surfaces
JP2534943B2 (ja) 1991-08-09 1996-09-18 三国重工業株式会社 グランドパツキン装置
US5217232A (en) * 1992-04-28 1993-06-08 Car-Graph, Inc. Thermally regulated segmented seal

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US670565A (en) * 1899-07-29 1901-03-26 Edwin Reynolds Piston-rod packing.
US1165486A (en) * 1911-11-15 1915-12-28 Robert Allen Packing for rods and the like.
US1819559A (en) * 1929-08-17 1931-08-18 British Metallic Packings Comp Metallic packing for reciprocating shafts
US3711104A (en) * 1971-03-16 1973-01-16 Dresser Ind Seal assembly
US3972640A (en) * 1974-09-16 1976-08-03 Miller Raphael W Highway joint with spring torsion bar
US6439578B1 (en) * 2000-04-10 2002-08-27 Hoerbiger Ventilwerke Gmbh Sealing ring combination

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8985588B2 (en) 2010-08-31 2015-03-24 Burckhardt Compression Ag Seal arrangement
US20150014945A1 (en) * 2013-07-12 2015-01-15 GM Global Technology Operations LLC Back-Up Ring Design "Split & Close"
CN105899859A (zh) * 2013-12-23 2016-08-24 伯克哈特压缩机股份公司 密封环
CN107701728A (zh) * 2017-11-07 2018-02-16 上海东方压缩机制造有限公司 压力平衡式填料环
KR20200123018A (ko) * 2019-04-18 2020-10-28 에어 프로덕츠 앤드 케미칼스, 인코오포레이티드 환형 실링 조립체
US10876634B2 (en) 2019-04-18 2020-12-29 Air Products And Chemicals, Inc. Annular sealing assembly
KR102382925B1 (ko) 2019-04-18 2022-04-04 에어 프로덕츠 앤드 케미칼스, 인코오포레이티드 환형 실링 조립체

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Publication number Publication date
CN101435507A (zh) 2009-05-20
AT505293B1 (de) 2008-12-15
EP2060833A1 (de) 2009-05-20
AT505293A4 (de) 2008-12-15

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AS Assignment

Owner name: HOERBIGER KOMPRESSORTECHNIK HOLDING GMBH, AUSTRIA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:LINDNER-SILWESTER, TINO;HOLD, CHRISTIAN;JANDL, ALEXANDER;REEL/FRAME:021993/0052

Effective date: 20081113

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION